Rotary machine

ABSTRACT

A torque receiving member is fixed to a rotary shaft of a compressor. A pulley, which is rotated by an external drive source, is rotatably supported by a housing of the compressor. The pulley is substantially coaxial with the torque receiving member. A rubber damper is located between the pulley and the torque receiving member. The rubber damper absorbs rotational vibration transmitted from the torque receiving member to the pulley. The pulley has a dynamic damper. The dynamic damper includes rollers, which swing like pendulums to reduce rotational vibration of the pulley. Stress produced due to displacement between the axis of the pulley and the torque receiving member is reduced by the rubber damper.

BACKGROUND OF THE INVENTION

[0001] The present invention relates to a rotary machine that includes ahousing, a rotary shaft, which is rotatably supported by the housing, afirst rotor, which is fixed to the rotary shaft, and a second rotor,which is rotatably supported by the housing. Specifically, the presentinvention pertains to a rotary machine that includes a first and secondrotors, which are substantially coaxial and coupled to each other.

[0002] For example, a typical vehicular compressor driven by an externaldrive source such as a vehicle engine has a first rotor, which is fixedto a rotary shaft for driving the compressor, and a second rotor, whichis coupled to the first rotor and to the engine by a belt. Typically,the second rotor is rotatably supported by the housing of the compressorwith a bearing. This structure reduces radial stress applied to therotary shaft due to the tension of the belt. Accordingly, the stressreceived by the bearing supporting the rotary shaft is reduced.

[0003] Japanese Laid-Open Patent Publication No. 2000-297844 disclosessuch a structure. The structure of the publication includes an inertialweight (second rotor) driven by an external drive source and a hub(first rotor) fixed to a crankshaft (rotary shaft). The inertial weightis coupled to the hub with an annular elastomer (damping member).

[0004] The annular elastomer attenuates the rotational vibrationtransmitted from the crankshaft to the inertial weight. Further, the hubhas a variable frequency vibration absorbing system. The system includescentrifugal weights, which swing like pendulums to reduce rotationalvibration of the crankshaft. Accordingly, the resonance between thefirst rotor and the second rotor is suppressed.

[0005] If the first rotor is fixed to a rotary shaft and the secondrotor is rotatably supported by a housing, which supports the rotaryshaft, the displacement between the axes of the first and second rotorsneeds to be absorbed (allowed). If there is no structure for absorbingthe axial displacement, the durability of bearings supporting the rotaryshaft and the durability of bearings supporting the second rotor aredegraded. The structure of the publication No. 2000-297844 does notabsorb such axial displacement.

SUMMARY OF THE INVENTION

[0006] Accordingly, it is an objective of the present invention toprovide a rotary machine that suppresses resonance between a first rotorand a second rotor and improves the durability of the rotary machine.

[0007] To achieve the foregoing and other objectives and in accordancewith the purpose of the present invention, a rotary machine driven by anexternal drive source is provided. The rotary machine includes ahousing, a rotary shaft, a first rotor, a second rotor, a couplingmember, and a dynamic damper. The rotary shaft is rotatably supported bythe housing. The first rotor is fixed to the rotary shaft to rotateintegrally with the rotary shaft. The second rotor is rotatablysupported by the housing. The second rotor is substantially coaxial withthe first rotor and is rotated by the external drive source. Thecoupling member couples the rotors to each other to transmit power fromthe second rotor to the first rotor. The coupling member includes adamping member. The dynamic damper is provided in at least one of therotors. The dynamic damper has a weight that swings like a pendulum. Theaxis of the pendulum motion of the weight is separated by apredetermined distance from and is substantially parallel to therotation axis of the corresponding rotor.

[0008] Other aspects and advantages of the invention will becomeapparent from the following description, taken in conjunction with theaccompanying drawings, illustrating by way of example the principles ofthe invention.

BRIEF DESCRIPTION OF THE DRAWINGS

[0009] The invention, together with objects and advantages thereof, maybest be understood by reference to the following description of thepresently preferred embodiments together with the accompanying drawingsin which:

[0010]FIG. 1 is a cross-sectional view illustrating a compressor havinga power transmission mechanism according to a first embodiment of thepresent invention;

[0011]FIG. 2(a) is a front view illustrating the power transmissionmechanism of the compressor shown in FIG. 1;

[0012]FIG. 2(b) is a cross-sectional view taken along line 2(b)-2(b) ofFIG. 2(a);

[0013]FIG. 3(a) is a front view illustrating a power transmissionmechanism according to a second embodiment; FIG. 3(b) is across-sectional view taken along line 3(b)-3(b) of FIG. 3(a);

[0014]FIG. 4(a) is a front view illustrating a power transmissionmechanism according to a second embodiment; FIG. 4(b) is across-sectional view taken along line 4(b)-4(b) of FIG. 4(a);

[0015]FIG. 5 is a front view illustrating a power transmission mechanismaccording to another embodiment;

[0016]FIG. 6 is a front view illustrating a power transmission mechanismaccording to another embodiment (the hub is omitted for purposes ofillustration); and

[0017]FIG. 7 is a front view illustrating a power transmission mechanismaccording to another embodiment (the hub is omitted for purposes ofillustration).

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0018] A compressor C according to one embodiment of the presentinvention will now be described with reference to FIGS. 1 to 2(b). Theleft end of the compressor C in FIG. 1 is defined as the front of thecompressor, and the right end is defined as the rear of the compressorC.

[0019] The compressor C forms a part of a vehicular air conditioner. Asshown in FIG. 1, the compressor C includes a cylinder block 11, a fronthousing member 12, a valve plate assembly 13, and a rear housing member14. The front housing member 12 is secured to the front end of thecylinder block 11. The rear housing member 14 is secured to the rear endof the cylinder block 11 with the valve plate assembly 13 in between.The cylinder block 11, the front housing 12, the valve plate assembly13, and the rear housing member 14 form the housing of the compressor C.

[0020] The cylinder block 11 and the front housing member 12 define acrank chamber 15 in between.

[0021] A rotary shaft, which is a drive shaft 16 in this embodiment, ishoused in the compressor housing and extends through the crank chamber15. The front portion of the drive shaft 16 is supported by a radialbearing 12A located in the front wall of the front housing member 12.The rear portion of the drive shaft 16 is supported by a radial bearing11A located in the cylinder block 11.

[0022] A cylindrical support 40 is formed at the front end of the fronthousing member 12. The front end portion of the drive shaft 16 extendsthrough the front wall of the front housing member 12 and is located inthe cylindrical support 40. A power transmission mechanism PT is fixedto the front end of the drive shaft 16. The power transmission mechanismPT includes a pulley 17. The front end of the drive shaft 16 is coupledto an external drive source, which is a vehicular engine E in thisembodiment, by the power transmission mechanism PT and a belt 18, whichis engaged with the pulley 17. The power transmission mechanism PT andthe compressor form a rotary machine.

[0023] A lug plate 19 is coupled to the drive shaft 16 and is located inthe crank chamber 15. The lug plate 19 rotates integrally with the driveshaft 16. A cam plate, which is a swash plate 20 in this embodiment, ishoused in the crank chamber 15. The swash plate 20 slides along andinclines with respect to the drive shaft 16. The swash plate 20 iscoupled to the lug plate 19 by the hinge mechanism 21. The lug plate 19permits the swash plate 20 to rotate integrally with the drive shaft 16and to incline with respect to the drive shaft 16 while sliding alongthe rotation axis of the drive shaft 16.

[0024] A snap ring 22 is fitted about the drive shaft 16. A spring 23extends between the snap ring 22 and the swash plate 20. The snap ring22 and the spring 23 limit the minimum inclination angle of the swashplate 20. At the minimum inclination angle of the swash plate 20, theangle defined by the swash plate 20 and the axis of the drive shaft 16is closest to ninety degrees.

[0025] Cylinder bores 24 (only one is shown in FIG. 1) are formed in thecylinder block 11. The cylinder bores 24 are located about the rotationaxis of the drive shaft 16. A single-headed piston 25 is reciprocallyhoused in each cylinder bore 24. The front and rear openings of eachcylinder bore 24 are closed by the associated piston 25 and the valveplate assembly 13. A compression chamber is defined in each cylinderbore 24. The volume of the compression chamber changes according to thereciprocation of the corresponding piston 24. Each piston 25 is coupledto the peripheral portion of the swash plate 20 by a pair of shoes 26.When the swash plate 20 is rotated by rotation of the drive shaft 16,the shoes 26 converts the rotation into reciprocation of each piston 25.

[0026] The cylinder block 11 (cylinder bores 24), the drive shaft 16,the lug plate 19, the swash plate 20, the hinge mechanism 21, thepistons 25, and the shoes 26 form a piston type variable displacementcompression mechanism.

[0027] Sets of suction ports 29 and suction valve flaps 30 and sets ofdischarge ports 31 and discharge valve flaps 32 are formed in the valveplate assembly 13. Each set of the suction port 29 and the correspondingsuction valve flap 30 and each set of the discharge port 31 and thecorresponding discharge valve flap 32 correspond to one of the cylinderbores 24 (compression chambers).

[0028] A suction chamber 27 and a discharge chamber 28 are defined inthe rear housing member 14. The front ends of the suction chamber 27 andthe discharge chamber 28 are closed by the valve plate assembly 13. Aseach piston 25 moves from the top dead center position to the bottomdead center position, refrigerant gas is drawn into the correspondingcylinder bore 24 (compression chamber) through the corresponding suctionport 29 while flexing the suction valve flap 30 to an open position. Lowpressure refrigerant gas that is drawn into the cylinder bore 24 iscompressed to a predetermined pressure as the piston 25 is moved fromthe bottom dead center position to the top dead center position. Then,the gas is discharged to the discharge chamber 28 through thecorresponding discharge port 31 while flexing the discharge valve flap32 to an open position.

[0029] The suction chamber 27 is connected to the discharge chamber 28by an external refrigerant circuit (not shown). Refrigerant that isdischarged from the discharge chamber 28 flows into the externalrefrigerant circuit. The external refrigerant circuit performs heatexchange using the refrigerant. The refrigerant is drawn into thesuction chamber 27 from the external refrigerant circuit. Then, therefrigerant is drawn into each cylinder bore 24 to be compressed again.

[0030] A bleed passage 33 is formed in the housing to connect the crankchamber 15 with the suction chamber 27. A supply passage 34 is formed inthe housing to connect the discharge chamber 28 with the crank chamber15. A control valve 35 is located in the supply passage 34 to regulatethe opening degree of the supply passage 34.

[0031] The opening of the control valve 35 is adjusted to control theflow rate of highly pressurized gas supplied to the crank chamber 15through the supply passage 34. The pressure in the crank chamber 15(crank chamber pressure Pc) is determined by the ratio of the gassupplied to the crank chamber 15 through the supply passage 34 and theflow rate of refrigerant gas conducted out from the crank chamber 15through the bleed passage 33. As the crank chamber pressure Pc varies,the difference between the crank chamber pressure Pc and the pressure inthe compression chambers varies, which changes the inclination angle ofthe swash plate 20. Accordingly, the stroke of each piston 25, or thecompressor displacement during one rotation of the drive shaft 16, isvaried.

[0032] As shown in FIGS. 1 to 2(b), the cylindrical support 40 protrudesfrom the front wall of the front housing member 12 and surrounds thefront portion of the drive shaft 16. The axis of the circumference ofthe support cylinder 40 substantially coincides with the axis of thedrive shaft 16.

[0033] A lip seal 41 is located in the support cylinder 40 to fill thespace between the support cylinder 40 and the drive shaft 16. The lipseal 41 prevents refrigerant from escaping the crank chamber 15 throughthe space between the support cylinder 40 and the drive shaft 16.

[0034] A first rotor, which is a torque receiving member 42 in thisembodiment, is secured to the front end of the drive shaft 16 to rotateintegrally with the drive shaft 16. The torque receiving portion 42includes a boss 42A and a circular hub 42B. The boss 42A is fitted inthe support cylinder 40 and is located forward of the lip seal 41. Thehub 42B is integrally formed with the boss 42A and is located forward ofthe support cylinder 40.

[0035] A second rotor, which is the pulley 17 in this embodiment, has abelt receiving portion 17A, about which the belt 18 is wound. The belt18 transmits power (torque) of the output shaft of the engine E to thepulley 17. The pulley 17 also has an inner cylinder 17B. A radialbearing 40A is fitted about the support cylinder 40. The outer ring ofthe radial bearing 40A is secured to the inner surface of the pulleyinner cylinder 17B. That is, the pulley 17 is rotatably supported by thehousing. Also, the pulley 17 rotates relative to the drive shaft 16 andthe torque receiving member 42 with the rotation axis of the pulley 17is coaxial with those of the drive shaft 16 and the torque receivingmember 42.

[0036] The inner surface of the inner cylinder 17B and the outer surfaceof the hub 42B are connected to each other by an annular elastic member(damping member), which is a rubber damper 43 in this embodiment. Therubber damper 43 is located in the power transmission path between thepulley 17 and the torque receiving member 42. The rubber damper 43functions as a coupling member for coupling the pulley 17 and the torquereceiving member 42 to each other. The rubber damper 43 is elasticallydeformed to allow the pulley 17 to move circumferentially and radiallyrelative to the torque receiving member 42.

[0037] Six weight receptacles 45 (only one is shown in FIG. 1) areformed in the pulley 17 between the belt receiving portion 17A and theinner cylinder 17B. The receptacles 45 function as receiving portions.The weight receptacles 45 are angularly spaced at the constantintervals.

[0038] Each weight receptacle 45 has a weight guiding surface 45A. Thecross-section of each of the guiding surfaces 45A is arcuate along aplane perpendicular to the rotation axis of the pulley 17. Each weightguiding surface 45A forms a part of an imaginary cylinder, the axis ofwhich is parallel to the rotation axis of the pulley 17. The radius ofthe imaginary cylinder is represented by r₁, and the axis of theimaginary cylinder is spaced from the rotation axis of the pulley 17 bya distance R₁.

[0039] A weight, which is a rigid roller 46 in this embodiment, isaccommodated in each weight receptacle 45. The diameter and the weightof each roller 46 are referred to as d₁ and m₁, respectively. Eachroller 46 rolls in the circumferential direction along the weightguiding surface 45A of the corresponding weight receptacle 45. Anannular lid 47 is fixed to the front face of the pulley 17 by bolts. Thelid 47 covers the weight receptacles 45 to prevent the rollers 46 fromfalling off the receptacles 45.

[0040] When the compressor C is being driven by the engine E, or whenthe drive shaft 16 is rotating, centrifugal force causes each roller 46to contact the corresponding guiding surface 45A (see FIGS. 1 to 2(b)).If torque fluctuation is generated due to, for example, torsionalvibrations of the drive shaft 16, each roller 46 starts reciprocatingalong the guiding surface 45A of the corresponding receptacle 45. Inother words, each roller 46 moves along the circumferential direction ofthe guiding surface 45A. That is, each roller 46, or the center ofgravity of each roller 46, swings like a pendulum about the axis of animaginary cylinder that includes the corresponding guiding surface 45A.That is, each roller 46 acts as a centrifugal pendulum when thecompressor C is being driven by the engine E. The size and mass of therollers 46 and the locations of the rollers 46 in the pulley 17 aredetermined such that the torque fluctuation is suppressed by pendulummotion of the rollers 46.

[0041] The pulley 17 (the weight receptacles 45) and the rollers 46 forma dynamic damper.

[0042] The settings of the rollers 46, which function as centrifugalpendulums, will now be described.

[0043] The rollers 46 suppress torque fluctuation when the frequency ofthe fluctuation is equal to the characteristic frequency of the roller46 (centrifugal pendulum). Therefore, the location, the size, and themass of the rollers 46 are determined such that the characteristicfrequency of the rollers 46 is set equal to the frequency of a peakcomponent of the torque fluctuation. Accordingly, the amplitude of thepeak component is suppressed, and the influence of the torquefluctuation is effectively reduced. A peak of the torque fluctuationrepresents a peak of the fluctuation range, or a rotation ordercomponent.

[0044] The frequency of the torque fluctuation and the characteristicfrequency of the rollers 46 are proportional to the angular velocity ω₁of the drive shaft 16, which corresponds to the speed of the drive shaft16. The frequency of the torque fluctuation when its range is thegreatest is represented by the product of the rotation speed of thedrive shaft 16 per unit time (ω₁/2π) and the number N of the cylinderbores 24. That is, the frequency is represented by the formula(ω₁/2π)·N. Through experiments, it was confirmed that an nth greatestpeak (n is a natural number) of the torque fluctuation has a value equalto a product n·(ω₁/2π) N.

[0045] The characteristic frequency of the rollers 46 is obtained bymultiplying the rotation speed of the drive shaft 16 per unit time(ω₁/2π) with the square root of the ratio R/r. The sign R represents thedistance between the rotation axis of the pulley 17 (a rotor havingweights that swing like pendulums) and the axis of the pendulum motionof each roller 46 (weight). The sign r represents the distance betweenthe center of the pendulum motion of each roller 46 and the center ofgravity of the roller 46.

[0046] Therefore, by equalizing the square root of the ratio R/r withthe product n·N, the characteristic frequency of each roller 46 isequalized with the frequency of the nth greatest peak of the torquefluctuation. Accordingly, the torque fluctuation at the nth greatestpeak is suppressed.

[0047] Accordingly, to suppress the greatest peak of the torquefluctuations, the value of the signs R and r are determined such thatthe square root of the ratio R/r is equal to N, or the value of theproduct n·N when n is one.

[0048] The torque produced about the rotation axis of the pulley 17 bythe rollers 46 is represented by a sign T. To effectively reduce peaksof the torque fluctuation by the pendulum motion of the rollers 46, thetorques T need to counter the torque fluctuation and the amplitudes ofthe torques T need to be equal to the amplitude of the peaks of thefluctuation. When the frequency of the peak of the torque fluctuationsis equal to the characteristic frequency of the rollers 46, the torque Tis represented by the following equation.

T=m·(ω_(a))²·(R+r)·R·φ  (Equation 1)

[0049] In the equation 1, the sign m represents the total mass of therollers 46 (m=6 m₁), and the sign ω_(a) represent the average angularvelocity of the rollers 46 when the rollers 48 swing in a minute angleφ.

[0050] In this embodiment, the mass m is maximized to minimize thevalues R, r, and φ, so that the size of the pulley 17 is minimized, andthe torque T is maximized.

[0051] The axis of each imaginary cylinder, which includes one of theguiding surfaces 45A, coincides with the axis, or the fulcrum, of thependulum motion of the corresponding roller 46. That is, the distance R₁between the rotation axis of the pulley 17 and the axis of eachimaginary cylinder corresponds to the distance R.

[0052] The distance between the axis of the pendulum motion of eachroller 46 and the center of gravity of the roller 46 is equal to thevalue obtained by subtracting the half of the diameter d₁ of the roller46 from the radius r₁ of the corresponding imaginary cylinder. That is,the difference (r₁−(d₁/2)) corresponds to the distance r.

[0053] To suppress the greatest peak of the torque fluctuation, thevalues of the distances R₁, r₁, and the diameter d₁ are determined suchthat the square root of R₁/(r₁−(d₁/2), which corresponds to the squareroot of the ratio R/r, is equal to N, or the value of the product n·Nwhen n is one.

[0054] The settings are determined by regarding each roller 46 as aparticle at the center of gravity.

[0055] The operation of the compressor C will now be described.

[0056] When the power of the engine E is supplied to the drive shaft 16through the pulley 17, the swash plate 20 rotates integrally with thedrive shaft 16. As the swash plate 20 rotates, each piston 25reciprocates in the associated cylinder bore 24 by a strokecorresponding to the inclination angle of the swash plate 20. As aresult, suction, compression and discharge of refrigerant gas arerepeated in the cylinder bores 24.

[0057] If the opening degree of the control valve 35 is decreased, theflow rate of highly pressurized gas supplied to the crank chamber 15from the discharge chamber 28 through the supply passage 34 isdecreased. Accordingly, the crank chamber pressure Pc is lowered and theinclination angle of the swash plate 20 is increased. As a result, thedisplacement of the compressor C is increased. If the opening degree ofthe control valve 35 is increased, the flow rate of highly pressurizedgas supplied to the crank chamber 15 from the discharge chamber 28through the supply passage 34 is increased. Accordingly, the crankchamber pressure Pc is raised and the inclination angle of the swashplate 20 is decreased. As a result, the displacement of the compressor Cis decreased.

[0058] During rotation of the drive shaft 16, the compression reactionforce of refrigerant and reaction force of reciprocation of the pistons25 are transmitted to the drive shaft 16 through the swash plate 20 andthe hinge mechanism 21, which torsionally (rotationally) vibrates thedrive shaft 16. The torsional vibrations generate torque fluctuation.The torque fluctuation causes the compressor C to resonate. The torquefluctuations also produce resonance between the compressor C andexternal devices (the engine E and auxiliary devices), which areconnected to the pulley 17 by the belt 18.

[0059] When the torque fluctuations are generated, the rollers 46 startswinging like pendulums. The pendulum motion of the rollers 46 producestorques about the rotation axis of the pulley 17. The produced torquessuppress the torque fluctuation. The characteristic frequency of therollers 46 is equal to the frequency of the greatest peak of the torquefluctuations. Therefore, the peak of the torque fluctuations issuppressed, which effectively reduce the torque fluctuations of thepulley 17.

[0060] Further, since the pulley 17 is coupled to the drive shaft 16(the torque receiving member 42) by the rubber damper 43, torquefluctuation transmitted from the torque receiving member 42 to thepulley 17 is attenuated. As a result, the resonance produced by thetorque fluctuations is effectively suppressed.

[0061] The rotation axes of the pulley 17 and the torque receivingmember 42 may be displaced from each other. However, since the rubberdamper 43 is located between the pulley 17 and the torque receivingmember 42 (the drive shaft 16), stress applied to the radial bearings12A, 40A due to the displacement of the axes is reduced.

[0062] The rubber damper 43 functions effectively when the frequency ofthe torque fluctuation is relatively high. The rollers 46 functioneffectively when the frequency of the torque fluctuation is relativelylow.

[0063] The present embodiment has the following advantages.

[0064] (1) The rollers 46 are provided in the pulley 17. Each roller 46swings like a pendulum about its axis, which is spaced from the rotationaxis of the pulley 17 by the predetermined distance R₁ and is parallelto the rotation axis of the pulley 17. The pendulum motion of therollers 46 suppresses the torsional vibration (the torque fluctuation),which suppresses resonance produced in the power transmission mechanismPT and the compressor C. Further, the pendulum motion suppressesresonance produced between the compressor C and the external devicesthat are coupled to the pulley 17 by the belt 18.

[0065] The rubber damper 43 is located in the power transmission pathbetween the pulley 17 and the torque receiving member 42. The rubberdamper 43 is elastically deformed to allow the pulley 17 to movecircumferentially relative to the torque receiving member 42, whichattenuates the torque fluctuation transmitted from the torque receivingmember 42 to the pulley 17. That is, in addition to the rollers 46, therubber damper 43 functions as a damper. Therefore, the resonance iseffectively suppressed.

[0066] Since the structure for suppressing resonance is provided in thepower transmission mechanism PT, the drive shaft 16 need not have anymeans for suppressing resonance. This reduces the weight and the size ofthe compressor C.

[0067] (2) Radial stress is applied to the drive shaft 16 due to thetension of the belt 18 coupling the pulley 17 with the engine E.However, since the pulley 17 is supported by the housing, radial stressapplied to the drive shaft 16 is reduced.

[0068] (3) The damper 43 is located between the pulley 17 and the torquereceiving member 42, or in the power transmission path in between. Therotation axes of the pulley 17 and the torque receiving member 42 (thedrive shaft 16) can be displaced from each other. However, since therubber damper 43 is elastically deformed to allow the pulley 17 to moveradially relative to the torque receiving member 42, deformation of therubber damper 43 reduces stress applied to the radial bearings 12A, 40Adue to the displacement of the axes. Therefore, the durability of therotary machine, which includes the power transmission mechanism PT andthe compressor C, is improved.

[0069] (4) The rollers 46, which are rigid cylinders, move along thearcuate weight guiding surface 45A formed in the weight receptacles 45of the pulley 17. Since the rollers 46 are not fixed to the fulcrum ofthe pendulum motion, the structure is simplified compared to a structurein which weights are fixed to the fulcrums. In a structure in which theweights are fixed to the fulcrums, the distance between each weight andthe corresponding pendulum axis (fulcrum) varies due to space createdbetween the fulcrum and the hole formed in the weight for receiving thefulcrum. The structure of the above embodiment has no such drawback.Therefore, the resonance is effectively suppressed.

[0070] A second embodiment of the present invention will now bedescribed. The second embodiment is the same as the first embodimentexcept for the structure of the power transmission mechanism PT. Mainly,the differences from the first embodiment will be discussed below, andsame or like reference numerals are given to parts that are the same asor like corresponding parts of the first embodiment.

[0071] As shown in FIGS. 3(a) and 3(b), a torque receiving member 42 ofthe second embodiment has a hub 42B. Compared to the first embodiment,the hub 42B has a greater diameter and substantially covers the entireopening of each receptacle 45. In the second embodiment, the lid 47 ofthe first embodiment is omitted. Instead, the hub 42B prevents therollers 46 from falling off the receptacles 45.

[0072] In the second embodiment, the rubber damper 43, which is locatedbetween the outer surface of the hub 42B and the inner surface of theinner cylinder 17B of the first embodiment, is omitted.

[0073] A damper receptacle 51 is formed between each adjacent pair ofthe weight receptacles 45. The front end of each damper receptacle 51 isopen. That is, the pulley 17 has the six damper receptacles 51.

[0074] A tubular elastic member (damping member), which is a rubberdamper 52, is fitted in each damper receptacle 51. The rubber dampers 52have circular cross-sections. The outer surface of each rubber damper 52closely contacts the inner surface of the corresponding damper recess51.

[0075] Each rubber damper 52 has a through hole 52A, the cross-sectionof which is circular. The hub 42B has power transmission pins 53projecting rearward. Each pin 53 corresponds to one of the rubberdampers 52. The rear end (right end as viewed in the drawings) of eachpin 53 is fitted in the through hole 52A of the corresponding damper 52.Each pin 53 is press fitted in a hole formed in the peripheral portionof the hub 42B, and extends in the axial direction of the torquereceiving member 42. The number of the pins 53 is six in thisembodiment.

[0076] Power transmitted from the engine E to the pulley 17 istransmitted to the torque receiving member 42 through the rubber dampers52 and the power transmission pins 53. The rubber dampers 52 and thepower transmission pins 53 are located in the power transmission pathbetween the pulley 17 and the torque receiving member 42. The rubberdampers 52 attenuate the torque fluctuation transmitted from the torquereceiving member 42 to the pulley 17.

[0077] In addition to the advantages (1) to (4), the second embodimenthas the following advantages.

[0078] (5) Each rubber damper 52 is located between one of the adjacentpairs of the weight receptacles 45. The spaces between the receptacles45 are effectively used for providing rubber dampers. The structure ofthe second embodiment reduces the axial size of the power transmissionmechanism PT compared to the first embodiment.

[0079] (6) The hub 42B of the torque receiving member 42 prevents therollers 46 from falling off the receptacles 45. Therefore, there is noneed for providing an additional member for preventing the rollers 46from falling, such as the lid 47 in the first embodiment. This reducesthe number of the parts and thus reduces the costs.

[0080] A third embodiment of the present invention will now bedescribed. The third embodiment is the same as the second embodimentexcept for the structures of the receptacles and the rollers and thelocation of the rubber dampers. Mainly, the differences from the secondembodiment will be discussed below, and same or like reference numeralsare given to parts that are the same as or like corresponding parts ofthe second embodiment.

[0081] As shown in FIGS. 4(a) and 4(b), the power transmission mechanismPT of the third embodiment has six receiving portions, which are weightreceptacles 55. An arcuate weight guiding surface 55A is formed in eachreceptacle 55. Each guiding surface 55A is a part of an imaginarycylinder the radius of which is larger than the radius r₁ of the guidingsurface 45A in the second embodiment.

[0082] An auxiliary guiding surface 55B is formed in each weightreceptacle 55. The auxiliary guiding surface 55B is separated from theguiding surface 55A toward the axis of the pulley 17 by a predetermineddistance and has an arcuate cross-section. As viewed from the front sideof the compressor C, each weight receptacle 55 appears as an arc havinga constant width with its middle portion located closer to the peripheryof the pulley 17 than its ends. Also, as viewed from the front side ofthe compressor C, each weight receptacle 55 is symmetrical with respectto an imaginary line that contains the rotation axis of the pulley 17and the center of the corresponding imaginary cylinder.

[0083] A weight, which is a rigid roller 56 in this embodiment, isaccommodated in each weight receptacle 55. The diameter of each roller56 is slightly less than the distance between the guiding surfaces 55Aand the auxiliary guiding surface 55B. The axial dimension of therollers 56 is slightly less than the depth of the receptacles 55, or thedimension along the axis of the pulley 17. That is, each roller 56 canmove along, or can swing like a pendulum in, the guiding surface 55A ofthe corresponding receptacle 55.

[0084] The rubber dampers 52 is located in the power transmission pathbetween the pulley 17 and the torque receiving member 42. Also, eachadjacent pair of the dampers 52 are located at the ends of the pendulummotion of one of the rollers 56, or at the ends of the correspondingreceptacle 55. Part of each rubber damper 52 is exposed in thecorresponding receptacles 55. The rubber dampers 52 and the receptacles55 form receiving portions. When the rollers 56 are moved by anexcessive degree, the rollers 56 contact the rubber dampers 52. That is,the rubber dampers 52 attenuate the torque fluctuation transmitted fromthe torque receiving member 42 to the pulley 17 and function as shockabsorbing members for absorbing the shock due to collision of eachroller 56 with the corresponding receiving portion.

[0085] Each rubber damper 52 is located between an adjacent pair of thereceptacles 55. The outer surface of each damper 52 is exposed in thecorresponding receptacles 55. That is, each damper 52 can contact therollers 56 in the corresponding pair of the receptacles 55.

[0086] The pulley 17 (the weight receptacles 55), the rubber dampers 52,and the rollers 56 form a dynamic damper.

[0087] In addition to the advantages (1) to (6), the third embodimenthas the following advantages.

[0088] (7) The rubber dampers 52 are located at the ends of the pendulummotion of each roller 56 in the receiving portions. Therefore, when eachroller 56 is moved by an excessive degree, the shock due to thecollision of the roller 56 and the corresponding receiving portion isabsorbed. This prevents the receiving portion and the roller 56 frombeing deformed or broken and suppresses noise.

[0089] (8) The rubber dampers 52 attenuate the torque fluctuationtransmitted from the torque receiving member 42 to the pulley 17 andfunction as shock absorbing members for absorbing the shock due tocollision of each roller 56 with the corresponding receiving portion.This structure facilitates creating of the spaces for the shockabsorbing members and the damping members and reduces the number of theparts, which reduces the costs.

[0090] (9) The shock absorbing member (each shock absorbing damper 52)is used for an adjacent pair of the receiving portions. This structurefacilitates creating of the spaces for the shock absorbing member (52)and reduces the number of the parts, which reduces the costs.

[0091] It should be apparent to those skilled in the art that thepresent invention may be embodied in many other specific forms withoutdeparting from the spirit or scope of the invention. Particularly, itshould be understood that the invention may be embodied in the followingforms.

[0092] A dynamic damper having weights that swing like pendulums may beprovided in the torque receiving member 42 instead of the pulley 17.Alternatively, both of the pulley 17 and the torque receiving member 42may have the dynamic damper.

[0093] In the illustrated embodiments, spherical weights may be used.

[0094] In the illustrated embodiments, the number of weight receptacles45, in which the rollers 46 are provided, may be changed. The number ofthe recesses need not correspond to the cylinder bores of the compressorC.

[0095] In the illustrated embodiments, the cross-sectional shape of eachreceptacle 45 along a plane perpendicular to the rotation axis of thepulley 17 may be circular. This facilitates machining of the receptacles45.

[0096] In the illustrated embodiments, the square root of the ratio R/ris equal to N, which is the value of n·N when the n is one. However, thesquare root of the ratio R/r may be the value of n·N when n is a naturalnumber that is equal to or more than two (for example, two or three).

[0097] In the illustrated embodiments, the ratio R/r, or the square rootof the ratio R/r, of the weights (rollers) may be different. In thiscase, since there are two or more values that correspond to the ratiosR/r, two or more peaks of the torque fluctuations are suppressed. Inthis case, the values of n are preferably selected from numbers in orderfrom one. For example, when three numbers are selected, one, two andthree are preferably used. Accordingly, the square roots of the ratiosR/r correspond to the numbers represented by the products n-N, in whichn is one, two and three. Therefore, the two or more greatest peaks ofthe torque fluctuation are suppressed. That is, the resonance iseffectively suppressed. FIG. 5 illustrates a power transmissionmechanism PT having a pulley 17 according to another embodiment. Thepulley 17 has a dynamic damper having two values of the ratio R/r.Specifically, two receptacles 61 and four receptacles 45 are formed inthe pulley 17. The cross-section of the receptacles 61 along a planeperpendicular to the axis of the pulley 17 is different from that of thereceptacles 45. The weight guiding surface 61A of each receptacle 61forms a part of an imaginary cylinder, the axis of which is parallel tothe rotation axis of the pulley 17. The radius of the imaginary cylinderis represented by r₂, and the axis of the imaginary cylinder is spacedfrom the rotation axis of the pulley 17 by a distance R₂. The values ofR₂ and r₂ and the diameter d₂ of a roller 62 accommodated in eachreceptacle 61 are determined such that the value corresponding to theratio R/r is different between the receptacle 61 and the receptacles 45.

[0098] In the illustrated embodiments, the weight guiding surface 45A isformed in each of the weight receptacle 45 in the pulley 17, and eachroller 46 swings like a pendulum along the corresponding guiding surface45A. However, the pulley may have weights each of which is coupled to afulcrum pin fixed to the pulley and swings like a pendulum.Alternatively, each weight may have a fulcrum pin, which is engaged witha hole formed in the pulley. In this case, each weight swings like apendulum about the pin.

[0099] In the illustrated embodiments, the settings are determined byregarding each weight as a particle at the center of gravity. However,the settings are preferably determined by taking the inertial mass ofeach weight into consideration. For example, in the case of thecylindrical rollers 46, the settings are preferably made based on theratio 2R/3r instead on the ratio R/r to take the inertial mass intoconsideration. When the frequency of the peak of the torque fluctuationis equal to the characteristic frequency of the rollers 46, the torque Tis represented by the following equation.

T=(3/2)·m·(ω_(a))²·(R+r)·R·φ  (Equation 2)

[0100] If spherical weights are used, the settings are preferably madebased on the ratio 5R/7r to take the inertial mass into consideration.When the frequency of a peak of the torque fluctuation is equal to thecharacteristic frequency of each spherical weight, the torque T isrepresented by the following equation.

T=(7/5)·m·(ω_(a))²·(R+r)·R·φ  (Equation 3)

[0101] If the weights are not formed cylindrical or spherical, thesettings are preferably made by taking the inertial mass of the weightsinto consideration so that the resonance is effectively suppressed.

[0102] In the second embodiment, each power transmission pin 53 may becoupled to the hub 42B with a tubular rubber damper. In other words, thepower transmission pins 53 may be coupled to both of the hub 42B and thepulley 17 with damping members such as rubber dampers.

[0103] In the second embodiment, each power transmission pin 53 is fixedto the hub 42B and coupled to the pulley 17 with the correspondingrubber damper 52. However, the pins 53 may be fixed to the pulley 17 andcoupled to the hub 42B with rubber dampers.

[0104] In the second embodiment, the rubber dampers 52 are tubular andhave circular cross-section. However, the cross-section of the rubberdampers 52 may be changed.

[0105] In the second embodiment, a space may exist between the innersurface of each receptacle 51 and the corresponding rubber damper 52 orbetween the inner surface of each rubber damper 52 and the outer surfaceof the corresponding power transmission pin 53. That is, narrow spacesmay exist as long as the power transmitting performance and thedurability of the power transmission mechanism PT are not adverselyaffected.

[0106] In the illustrated embodiments, the rubber dampers (43, 52) areused. However, dampers made of elastomer may be used.

[0107] In the illustrated embodiment, rubber dampers (43, 52) are usedas damping members. However, the pulley 17 may be coupled to the torquereceiving member 42 by springs (damping members (elastic members)) suchas metal springs. FIG. 6 describes such an embodiment. In the embodimentof FIG. 6, the rubber dampers 52 of the second embodiment are replacedwith leaf springs 71. The leaf springs 71 transmit power from the pulley17 to the power transmission pins 53. In FIG. 6, the hub 42B is omittedfor purposes of illustration. In the structure of FIG. 6, a springreceptacle 72 is formed between each adjacent pair of the weightreceptacles 45. A plurality of leaf springs 71 are located in eachspring receptacle 72. The rear portion of each power transmission pin 53is inserted in one of the spring receptacle 72. In each springreceptacle 72, two of the rectangular springs 71 are laminated andlocated at each side of the power transmission pin 53 in thecircumferential direction of the pulley 17. The ends of the springs 71(the ends in the radial direction of the pulley 17) are engaged withsteps 72A formed in the inner wall of the spring receptacle 72, whichprevents the power transmission pin 53 from moving toward the oppositeside in the circumferential direction. The middle portions of thesprings 71 are elastically deformed by the power transmission pin 53,which absorbs the torque fluctuation transmitted from the torquereceiving member 42 to the pulley 17. The friction between the laminatedsprings 71 attenuates the torque fluctuation. The rotation axes of thepulley 17 and the torque receiving member 42 may be displaced from eachother. However, deformation of the springs 71 and the changes of thecontact point between the springs 71 and the pins 53 reduce stressapplied to the radial bearings 12A, 40A due to the displacement of theaxes.

[0108] In the illustrated embodiments, rubber dampers (43, 52) are usedas damping members. However, the pulley 17 may be coupled to the torquereceiving member 42 by damping members having gel containers. FIG. 7describes such an embodiment. In the embodiment of FIG. 7, the powertransmission pins 53 of the second embodiment, which are located betweenthe pulley 17 and the hub 42B, are replaced with power transmissionprojections 73 and containers 74. The power transmission projections 73project rearward from the hub 42B. The pulley 17 is coupled to thetorque receiving member 42 by the projections 73 and the containers 74.In FIG. 7, the hub 42B is omitted for purposes of illustration. In thestructure of FIG. 7, a container receptacle 75 is formed between eachadjacent pair of the weight receptacles 45. A plurality of containers 74are located in each container receptacle 75. The cross-section of eachpower transmission projection 73 along a plane perpendicular to therotation axis of the torque receiving member 42 is substantiallyrectangular. The rear portion of each projection 73 is inserted in thecorresponding container recess 75. In each container receptacle 75, acontainer 74 is located at each side of the projection 73 in thecircumferential direction of the pulley 17. Each container 74 includes abag-like member and gel, which is included in the bag-like member. Inthis structure, gel sealed in the gel containers 74 attenuates thetorque fluctuation transmitted from the torque receiving member 42 tothe pulley 17 through the projections 73. The rotation axes of thepulley 17 and the torque receiving member 42 may be displaced from eachother due to errors. However, deformation of the gel containers 74reduces stress applied to the radial bearings 12A, 40A due to thedisplacement of the axes. Instead of the gel containers, containershaving fluid such as liquid or gas may be used as damping members. Iffluid is used, the same advantages as the case where gel is used areachieved. However, gel attenuates vibration by a greater degree comparedto fluid.

[0109] The number of cylinder bores 24 in the compressor C may bechanged. A typical compressor for a vehicular air conditioner has threeto seven cylinder bores. If the number of the cylinder bores 24 isthree, the fluctuation of torque transmitted between the pulley 17 andthe torque receiving member 42 due to rotational vibration produced inthe drive shaft 16 is greater compared to a case where the number of thecylinders 24 is four or greater. That is, in a rotary machine that hasthree cylinder bores, the dynamic dampers and the damping members of theillustrated embodiment effectively suppress resonance.

[0110] In the third embodiment, each shock absorbing members (52) neednot be used for an adjacent pair of the guides. Each shock absorbingmembers may correspond to one of the guides.

[0111] In the third embodiment, the rubber dampers 52 attenuate thetorque fluctuation transmitted from the torque receiving member 42 tothe pulley 17 and also function as shock absorbing members for absorbingthe shock due to collision of each roller 56 with the correspondingreceiving portion. However, the damping members may be providedseparately from the shock absorbing members.

[0112] In the illustrated embodiments, the shock absorbing members fordamping shock due to collision between the guides and the weights may beprovided at a position other than the ends of pendulum motion of eachweight. For example, the shock absorbing members may be provided on anysurface forming each receptacle (45, 55, 61). In the first embodiment,the shock absorbing members may be provided on a side of the lid 47 thatfaces the receptacles. In the second and third embodiments, the shockabsorbing members may be located on a side of the hub 42B that faces thereceptacles. In these cases, rubber sheets or elastic coating may beused as the shock absorbing members. The shock absorbing members dampenthe shock due to collision between the weights and the guides. Theweights collide with the guiding surface (45A, 55A, 61A) of thereceptacles when, for example, the pulley 17 suddenly starts rotating ata high speed. When the rotation speed of the pulley 17 is decreasedwhile the weight contacts and is swinging like a pendulum along theguiding surface, the weight is separated from the guiding surface. Atthis time, the weight collides with the radially inner surface of thereceptacle (for example, the auxiliary guiding surface 55B).

[0113] In the illustrated embodiment, the power transmission mechanismPT is used for the compressor C, which has the single headed pistons 25.However, the mechanism PT may be used for a compressor that hasdouble-headed pistons. In this type of compressor, cylinder bores areformed on either side of a crank chamber and each piston compresses gasin one of the pairs of the cylinder bores.

[0114] In the illustrated embodiment, the cam plate (the swash plate 20)rotates integrally with the drive shaft 16. However, the pulley 17 maybe used in a compressor, in which a cam plate rotates relative to adrive shaft. For example, the pulley 17 may be used in a wobble typecompressor.

[0115] The pulley 17 may be used in a fixed displacement typecompressor, in which the stroke of the pistons are not variable.

[0116] In the illustrated embodiments, the present invention is appliedto a reciprocal piston type compressor. However, the present inventionmay be applied to rotary compressors such as a scroll type compressor.

[0117] In the illustrated embodiment, the second rotor is the pulley 17.However, a sprocket or a gear may be used as the first rotor.

[0118] In the illustrated embodiments, the present invention is appliedto the compressor C. However, the present invention may be applied toany apparatus that has a rotary shaft coupled to the power transmissionmechanism PT, and torsional vibration is produced in the rotary shaft.

[0119] The axis of the pendulum motion of each weight need not beparallel to the rotation axis of the rotor in which the weights arelocated. Specifically, the axis of the pendulum motion may be inclinedrelative to the rotation axis of the rotor in a range in which themaximum torque fluctuation is suppressed by a desirable degree.

[0120] Therefore, the present examples and embodiments are to beconsidered as illustrative and not restrictive and the invention is notto be limited to the details given herein, but may be modified withinthe scope and equivalence of the appended claims.

1. A rotary machine comprising: a housing; a rotating shaft rotatablysupported by the housing; a first rotor rotatably fixed to the rotatingshaft and integrally rotatable therewith outside the housing; a secondrotor rotatably supported on the housing outside the housing andoperably connected to the first rotor in a state substantially coaxialto the first rotor; and an absorption mechanism, arranged on aconnecting portion of the first rotor and the second rotor, forabsorbing misalignment between the axis of the first rotor and the axisof the second rotor, the absorption mechanism being formed from a rigidmember.
 2. The rotary machine as claimed in claim 1, wherein theabsorption mechanism includes: a support member rotatably supported onone of the first rotor and the second rotor, the support member beingrotatably supported on that rotor about an axis parallel to a rotationaxis of the rotor supporting the support member; and an eccentric pin,arranged relatively rotatable to at least one of the other one of thefirst rotor and the second rotor and the support member, for connectingthe other one of the two rotors and the support member, the eccentricpin being arranged eccentric to an axis of the support member by aneccentricity amount that is greater than an amount of axis misalignmentbetween the two rotors so that the axis of the other one of the tworotors does not overlap the axis of eccentric pin.
 3. The rotary machineas claimed in claim 1, wherein the absorption mechanism includes: aconnecting pin projecting from one of the two rotors and having an axisparallel to a rotation axis of that rotor; and an elongated hole-like orgroove-like connecting portion formed on the other one of the two rotorsso as to generally extend in a radial direction of that rotor and facethe connecting pin, wherein the connecting pin is inserted into theconnecting portion so as to be slidable along the connecting portion androtatable within the connecting portion.
 4. The rotary machine asclaimed in claim 1, further comprising a compression mechanism forcompressing refrigerant based on rotation of the rotating shaft.
 5. Therotary machine as claimed in claim 4, wherein the compression mechanismis a piston-type compression mechanism.
 6. The rotary machine as claimedin claim 4, wherein the compression mechanism is formed so that theamount of refrigerant discharges per one rotation of the rotating shaftis variable.
 7. The rotary machine as claimed in claim 5, wherein thecompression mechanism is formed so that the amount of refrigerantdischarges per one rotation of the rotating shaft is variable.
 8. Therotary machine as claimed in claim 2, further comprising a compressionmechanism for compressing refrigerant based on rotation of the rotatingshaft.
 9. The rotary machine as claimed in claim 3, further comprising acompression mechanism for compressing refrigerant based on rotation ofthe rotating shaft.